Trenching Tech Advancements Coming to the Jobsite. Rock saw trenching

US6547337B2. Trencher with foldable rock saw wheel. Google Patents

Publication number US6547337B2 US6547337B2 US09/942,141 US94214101A US6547337B2 US 6547337 B2 US6547337 B2 US 6547337B2 US 94214101 A US94214101 A US 94214101A US 6547337 B2 US6547337 B2 US 6547337B2 Authority US United States Prior art keywords section wheel trencher rock saw connecting plate Prior art date 2001-08-29 Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.) Expired. Fee Related Application number US09/942,141 Other versions US20030042785A1 ( en Inventor Johnnie C. Welch, Jr. Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.) Tesmec USA Inc Original Assignee Tesmec USA Inc Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.) 2001-08-29 Filing date 2001-08-29 Publication date 2003-04-15 2001-08-29 Application filed by Tesmec USA Inc filed Critical Tesmec USA Inc 2001-08-29 Priority to US09/942,141 priority Critical patent/US6547337B2/en 2001-08-29 Assigned to TESMEC USA, INC. reassignment TESMEC USA, INC. ASSIGNMENT OF ASSIGNORS INTEREST (SEE DOCUMENT FOR DETAILS). Assignors: WELCH, JOHNNIE C., JR. 2003-03-06 Publication of US20030042785A1 publication Critical patent/US20030042785A1/en 2003-04-15 Application granted granted Critical 2003-04-15 Publication of US6547337B2 publication Critical patent/US6547337B2/en 2021-08-29 Anticipated expiration legal-status Critical Status Expired. Fee Related legal-status Critical Current

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Classifications

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F3/00 — Dredgers; Soil-shifting machines
E02F3/04 — Dredgers; Soil-shifting machines mechanically-driven
E02F3/18 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
E02F3/188 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with the axis being horizontal and transverse to the direction of travel

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F3/00 — Dredgers; Soil-shifting machines
E02F3/04 — Dredgers; Soil-shifting machines mechanically-driven
E02F3/18 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
E02F3/20 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with tools that only loosen the material, i.e. mill-type wheels

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F3/00 — Dredgers; Soil-shifting machines
E02F3/04 — Dredgers; Soil-shifting machines mechanically-driven
E02F3/18 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
E02F3/22 — Component parts
E02F3/24 — Digging wheels; Digging elements of wheels; Drives for wheels
E02F3/241 — Digging wheels; Digging elements of wheels; Drives for wheels digging wheels

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F5/00 — Dredgers or soil-shifting machines for special purposes
E02F5/02 — Dredgers or soil-shifting machines for special purposes for digging trenches or ditches
E02F5/08 — Dredgers or soil-shifting machines for special purposes for digging trenches or ditches with digging wheels turning round an axis

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F9/00 — Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00. E02F7/00
E02F9/003 — Devices for transporting the soil-shifting machines or excavators, e.g. by pushing them or by hitching them to a tractor

Y — GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
Y10 — TECHNICAL SUBJECTS COVERED BY FORMER USPC
Y10T — TECHNICAL SUBJECTS COVERED BY FORMER US CLASSIFICATION
Y10T83/00 — Cutting
Y10T83/929 — Tool or tool with support
Y10T83/9319 — Toothed blade or tooth therefor
Y10T83/9326 — Plural separable sections

Abstract

A trencher with a rock saw wheel has a foldable section that may be pivoted to one side during transport of the trencher on a truck or trailer, in order to decrease the overall height of the trencher during transport, or can be removed to reduce transport weight.

Description

The present invention relates generally to the field of trenchers, and more particularly to a trencher with a foldable rock saw wheel.

There are basically three types of trenching machines; bucket wheel, chain type, and disk (or saw). Bucket wheels are basically for softer materials, and the chain type and disk type are better suited for hard rock trenching, but all can be used for soft material trenching. A typical chain or saw trencher has a digging boom or frame that is connected to a tractor. Chain type trenchers are capable of much wider and deeper trenching than the disk type. However, they have two problems. First, the chain will wear much quicker. Second, a wider trench must be cut in order to provide clearance for the chain. The disk or saw type trencher typically cuts shallower and narrower than an equivalent size chain type trencher. It has a rigid wheel, typically in the form of a round, solid metal disk, and cutters attached around the wheel’s outer circumference or periphery.

As a disk wears much better than a chain, the total cost of using a disk or saw for trenching can be significantly less. However, digging deeper trenches requires use of a larger diameter saw. Because a trencher with a large saw must be transported to a digging site on the back of a trailer, with the saw mounted on the boom, height restrictions on public roadways limit the size or diameter of a rock saw on a trencher. Many trenchers are designed to allow use of both saw and chain attachments. Deeper trenches are preferred for burying fiber optic and other comparatively fragile cables. Doing so reduces the risk of the cable being accidentally cut during subsequent construction.

The present invention concerns an improved saw for a trenching machine. According to the invention, a trenching machine includes a rock saw wheel with at least one section that can be folded and/or removed. This separate section permits transporting a trenching machine with a rock saw wheel that would otherwise be too large for transport or to obtain a permit for transport on public roadways without completely disassembling the wheel. Thus, deeper trenches can be dug using a saw or disk trencher with a lower total cost of operation.

One example of a trenching machine employing one or more teachings of the invention has a rock saw wheel with at least one section or piece separate from a main portion of the wheel. The main portion of the wheel is mounted to the trencher. At least one of the one or more separate sections is attached to the main portion during normal operation by one or more connecting plates that span at least a portion of a seam where the foldable section abuts the main portion of the wheel. One or more removable fasteners—bolts, for example—connect the plate(s) to the main portion and to a section. The plates thereby provide rigidity to the wheel for operation. The fasteners are removed to allow the separate section to be folded to a side or removed altogether, which reduces the diameter of the rock saw in one direction to a size that allows for transport over public roadways.

It is preferred that one connecting plate for at least one separate section be attached at one end to the main portion so that it pivots, such as by use of a hinge or similar mechanism. Thus, the separate section remains connected to the main portion of the wheel, but folded or pivoted to the side during transport of the trenching machine. With a pivoting connection, the separate section can be swung into place and assembled for operation with fewer steps and without, in the case of very large wheels, the need for additional lifting equipment. It also avoids having to separately stow the section on the trailer. Furthermore, it is preferred that the pivoting connection be of a type that permits disconnecting the separate section for removal should a reduction in transport weight as well as a height reduction be needed.

A preferred embodiment of the invention is further described below with reference to the accompanying drawings.

FIG. 3a is a sectional view of the rock saw wheel of FIG. 2, taken along section line 3 a—3 a, with a separable section of the wheel shown connected to a main portion of the wheel and in a normal operating configuration;

FIG 3 b is a sectional view of the rock saw wheel of FIG. 2, taken along section line 3 a—3 a, with certain bolts removed as a first step in folding the separable section;

FIG. 3c is a sectional view of the rock saw wheel of FIG. 2, taken along section line 3 a—3 a, with the separble section folded but still connected;

FIG. 3d is a sectional view of the rock saw wheel of FIG. 2, taken along section line 3 a—3 a, with the separable section separated following removal of hinge pins.

Like numerals reference like and corresponding parts throughout the drawings. Referring to FIG. 1, trenching machine or trencher 100 is an example of a trenching machine. It is intended only to be representative of a trenching machine with which the teachings of the invention may be used. The trencher includes a cab 102, in which an operator sits, at least one motor 104, a pair of crawlers 106 for locomotion, and a structure for supporting and lowering and raising a rock saw such as a pivoting boom 108, which is shown in FIG. 1. The illustrated rock saw is an example of a type of saw that has a disk-shaped wheel, generally designated 110. Although shown as a solid disk, the wheel need not be entirely solid, but could have portions cut out if weight reduction was desired. The wheel could be made of an assembly of structure members as a wheel, though a disk is easier to make into a wheel suitable for digging trenches. It is stronger and less prone to failure.

Wheel 110 has at least two separate sections. In the illustrated example, it has a main or central portion or section 110 a and at least one secondary section 110 b. Each junction or split between the separate sections of the wheel may occur anywhere that, when one portion is removed or turned to a side, the diameter of the wheel is reduced, thereby resulting in its overall height being able to be lowered for transport when it is attached to the trencher. However, it is preferable that the junction between the pieces not intersect the area of the wheel at which it is coupled to a rotary power source, as doing so introduces additional stresses at the point of coupling that are undesirable. Furthermore, for structural reasons, it is also preferrable for the junction to be located as far as possible from the center of the wheel while still allowing for the desired lowering in height. A plurality of cutting tools 112 is attached around the outer circumference or perimeter of the wheel. These tools are, preferably, suitable for cutting rock and other hard geological formations. Many examples of such tools are known. A transmission, of which gear train 114 is a part, couples rotary power from the engine to a rotary output by hydraulic or mechanical means. Hub 116 of wheel 110 is coupled to this rotary output. Hub 116 of the wheel preferably includes a reinforcing disk 122. The hub and disk are attached to the main section of the wheel by bolts 123, but could be attached by other means, including welds. Boom 108 pivots about axis 118 in order to raise it for transport and lower it for trenching. Hydraulic piston and cylinder 120 is an example of one means for raising and lowering the boom. Any means suitable for raising and lowering the boom and rock saw may be employed in place of hydraulic piston and cylinder 120. The boom is shown in a lowered position. Although a boom is more advantageous, other means for lowering and raising the wheel may be employed, such as a gantry and slide.

Referring to FIGS. 1, 2, and 3 a, 3 b, 3 c and 3 d, bars 124 do not allow material build-up between the wheel and the ditch while cutting. A second set of bars 124, which cannot be seen in FIGS. 1 or 2, are attached to the other side of the wheel, opposite the visible ones. These cleaning bars are arrayed symmetrically about the center of the wheel and extend along the radii of the wheel. They are preferably attached by bolts 126, secured by nuts, to the wheel, but are not required to be. Cutting tools 112 are preferably held by a plurality of removable tool holders 128, each of which is attached by a suitable fastener, such as one or more bolts 130, secured with nuts, to the outer diameter or circumference of the wheel. In the illustrated example, each tool holder carries more than one cutting tool, though each could be made to hold only one if desired.

At least one, and preferably two, connecting plates, 136 and 140 join sections 110 a and 110 b for operation of the rock saw. The connecting plate(s) span the junction of the sections on opposite sides of the wheel. Releasable fasteners, such as bolts or screws 146, attach the connecting plates to the wheel. Each bolt preferably passes through both connecting plate(s) and the main portion or the foldable section. The bolts on at least one side of the junction of the main portion and foldable section are loosened and removed to allow the foldable section to be folded to one side.

It is preferred that main section 110 a be attached to secondary section 110 b in a manner that allows the secondary section to be pivoted to one side for transport, yet remain attached to the main section. One or more hinges to couple the two sections for pivoting. Having the secondary section remain attached allows it to be relatively easily swung to one side for transport, and then back again for assembly. In a preferred embodiment that is illustrated, multiple hinges 132 are used, as it is easier to assemble. However, a single hinge can be used in its place, and no form of hinge is required. One side of hinge 132 is, in the example, attached to bar 134, which in turn is welded to main portion 110 a of the wheel, the other edge of hinge 132 is welded directly to main portion 110 a of the wheel. The other side of hinge 132 is attached to connecting plate 136. Connecting plate 136 spans the junction of the two sections, 110 a and 110 b, of the wheel 110 when the wheel is operational. Plate 136 is attached to secondary section 110 b, preferably by direct welding though it could be attached in other ways. Bar 138 is attached, preferably by a weld, to main section 110B for strength and erosion control. Connecting plate 140 is placed on the opposite of the junction. It is attached to main section 110 a of the wheel, preferably by direct welding to section 110 a. Bar 142, which is attached to the wheel, preferably by a weld, balances bar 134, which is on the opposite side of the wheel, and protects plate 140 from erosion. Bar 144, which is attached to the wheel, preferably by a weld, balances bar 138 which is on the opposite side of the wheel, and protects plate 140 from erosion and prevents debris from entering the joint. Thus, when threaded bolts 146 are removed, as shown in FIG. 3b, and the tool holders 128 (see FIG. 2) spanning the joint are removed, the secondary section 110 b of the wheel can be swung to one side, as shown in FIG. 3c. Pins 148 can also be removed from the hinge 132, allowing sections 110 a and 110 b to be separated should a weight reduction as well as a height reduction be needed, as shown in FIG. 3d. Plates 150 are located on both sides of the wheel, opposite the shaft for balance during rotation, as shown in FIG. 3.

If additional height clearance is required for transport, wheel 110 could include an additional secondary section, located opposite of the hub of the wheel from secondary section 110 b. Generally, it is preferably not to have the seam or junction between sections of the wheel run through the wheel’s hub in order to avoid having to detach a portion of the wheel from the hub.

While the invention has been particularly shown and described by the foregoing detailed description, it will be understood by those skilled in the art that various other changes in form and detail may be made without departing from the spirit and scope of the invention.

Claims ( 11 )

A rock saw wheel for a trencher, the rock saw wheel comprising a wheel for supporting a plurality of cutting elements around its periphery; the wheel having a first section for attaching to a rotary power source and at least one second section that, when placed in a common plane with the first section, establishes a round wheel and, if one of the at least one second section is removed, reduces the wheel’s diameter along at least one direction; the one of the at least one second section being joined to the first section by at least one connecting plate attached to the first section and/or the one of the at least one second section by at least one releasable fastener.

The rock saw wheel of claim 1. wherein the one of the at least one second section is pivotally connected to the first section, whereby the one of the at least one second section may be pivoted toward one side of the wheel while remaining connected to the first section.

The rock saw wheel of claim 1. wherein the connecting plate is attached to either the first section or the one second section by at least one hinge.

The rock saw wheel of claim 1 further comprising another connecting plate for joining the one of the at least one second section to the first section on a side of the wheel opposite the at least one connecting plate.

The rock saw of wheel of claim 1 wherein the one of the at least one second section is removable for reducing transport weight as well as height.

wherein, the rock saw wheel comprises a wheel, around which is disposed a plurality of cutting elements; the wheel having a first section and at least one second section that, if removed, reduces the wheel’s diameter along at least one direction; one of the at least one second section being joined to the first section by at least one connecting plate attached to the first section and/or the one of the at least one second section by at least one releasable fastener.

The rock saw wheel of claim 6. wherein the one of the at least one second section is pivotally connected to the first section.

The rock saw wheel of claim 6. wherein the connecting plate is connected to at least one of the first section and the one of the at least one second section by at least one hinge.

The rock saw of wheel of claim 6 further comprising another connecting plate joining the one of at least one second section to the first section on a side of the wheel opposite the at least one connecting plate.

A method for transporting over roadway a trencher, the trencher having rotationally mounted to it a foldable rock saw, the rock saw including a wheel, around which is disposed a plurality of cutting elements; the wheel having a first section and at least one second section that, if removed, reduces the wheel’s diameter along at least one direction; one of the at least one second section being pivotally connected to the first section so that the one of the at least one second section may be pivoted toward one side of the wheel while remaining connected to the first section, the method comprising:

pivoting the one of the at lest one second section to one side of the wheel in order to reduce the trencher’s overall height;

pivoting the one of the at least one second section so that it is in a common plane with the first section at the site; and

joining the first section and the one of the at least one second section by at least one connecting plate in order to prevent pivoting during trenching operation.

The method of claim 10 further comprising unfastening the one of the at least one second section from the first section prior to transporting the trencher and refastening the one of the at least one second section to the first section after transporting.

US09/942,141 2001-08-29 2001-08-29 Trencher with foldable rock saw wheel Expired. Fee Related US6547337B2 ( en )

Family

Cited By (7)

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Publication number Priority date Publication date Assignee Title

US7056188B1 ( en )	2002-07-29	2006-06-06	Robinson Brick Company	Rock saw
US20060117611A1 ( en )	2004-12-08	2006-06-08	Yoder Shaun L	Excavating machine for rocky and other soils
US20080236560A1 ( en )	2007-03-30	2008-10-02	Schlough Michael P	Corner saw
US20090263195A1 ( en )	2008-04-16	2009-10-22	Jeff Horan	Trenching and drain installation system and method
US20100139469A1 ( en )	2007-03-14	2010-06-10	Paul Matteucci	Cutting tool
US9394654B2 ( en )	2012-07-27	2016-07-19	DAVID L. PERKINS, Jr.	Track driven slab saw
US10201914B2 ( en )	2015-01-20	2019-02-12	Park Industries, Inc.	Material loading apparatus

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Legal Events

Owner name: TESMEC USA, INC., TEXAS

Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNOR:WELCH, JOHNNIE C., JR.;REEL/FRAME:012132/0457

Effective date: 20010828

Free format text: PATENT EXPIRED DUE TO NONPAYMENT OF MAINTENANCE FEES UNDER 37 CFR 1.362

Effective date: 20150415

Trenching Tech Advancements Coming to the Jobsite

Ride-on trencher manufacturers have focused on making equipment that is more versatile and easier to use. The timing is perfect, given that demand for underground infrastructure and broadband continues running hot, and the availability of skilled equipment operators continues running thin.

One manufacturer, Ditch Witch, has placed considerable emphasis on making its ride-on trenchers more versatile, allowing contractors to tackle more projects with the same machine. For example, the RT80 and new RT70 tractors feature a more modular design. This allows for the use of either tires or tracks.

“Utility contractors have always been able to change rear attachments to take on different jobs,” says Steve Seabolt, Heavy-Duty Tractor Product Manager at Ditch Witch. “But to operate with either tires or tracks, there has always been a need for two machines. Now it’s just a matter of bolting them on and changing a setting in the software.”

Technology from Vermeer is designed to simplify the process of switching attachments. Vermeer’s i2 denotes “interchangeability and intelligence”. It’s currently available on the RTX1250i2 and XTS1250i2 ride-on utility tractors.

“The interchangeability piece relates to the attachments,” says Ed Savage, Lead Product Manager at Vermeer. “If you’re using a trenching attachment, for instance, i2 makes it easier to switch to a plow or rock wheel just by the way we’ve designed the mounting.”

With the intelligence piece, i2 electronically knows which attachment is on the tractor, allowing it to instinctively change parameters such as pressure settings to ensure optimum operation. “The operator doesn’t have to worry about any of that anymore, which makes the machine much easier to operate,” Savage points out.

Smarter, more automated trenching

With the skill level of some of today’s newer operators, it can take quite a bit of training before they become productive. Manufacturers like Vermeer and Ditch Witch have taken aim at this common contractor pain point.

TrenchSense is one example from Vermeer. When running a trenching attachment, operators will often hit things like rocks and tree roots which typically stall out the digger chain. TrenchSense simplifies the process of escaping an obstruction.

“Traditionally, the operator would have to stop the machine and put the digger chain back to neutral, back the machine up, raise the boom, re-engage the digger chain, and attempt moving forward again to work through the obstruction,” Savage explains. “TrenchSense automates that entire process.”

Ditch Witch has developed a technology with similar functionality.

“Ditch Witch anti-stall technology allows the operator to simply push a button to initiate a sequence of stopping the ground drive, backing the tractor up slightly, and reversing the digging chain rotation to clear the obstruction,” Seabolt explains. “Then the machine resumes forward rotation of both the chain and ground drive.”

Another Vermeer innovation is Auto Plunge. Savage says this technology aims to address the difficulty many new operators have when executing their initial cut with a trenching attachment or rock saw.

“It’s pretty easy to stall out the cutting chain if you don’t do it right,” Savage points out. “Auto Plunge senses engine rpm. If it notices that the engine is starting to pull down, it eases up on how fast it is plunging into the ground.”

Ditch Witch has developed a Trench Depth Meter. This technology tells the operator how far and deep they are trenching in real-time, eliminating the inefficient process of using tape measures and measuring wheels.

“Trench Depth also has some logging capability where the operator can see history,” Seabolt points out. “Data can be pulled off of the machine and onto a USB drive. Combined with separate GPS mapping data, this can feed into the customer’s as-built system or GIS system.”

The Ditch Witch Trench Depth Meter is currently an optional feature on the RT70 tractor. However, the company plans to offer this in additional tractor models soon.

Smarter powertrain management

As Vermeer’s Savage explains, every engine has a certain range of rpm’s where it develops the most torque and is the most productive. Vermeer’s Productivity Zone technology finds that sweet spot without burdening the operator.

“In the past, we had something called ‘auto creep’ where different settings, switches, and dials allowed the operator to manually set everything to get the most productivity,” Savage explains. “But operators were constantly having to adjust things. With Productivity Zone, this is done automatically. It keeps the engine in that most productive window so the operator doesn’t even have to think about it anymore.”

EcoIdle is another intelligent technology from Vermeer. If the tractor senses that a machine function hasn’t been activated for 15 seconds, such as engagement of the ground drive or an attachment, it will automatically take the engine down to a slow idle. This helps the operator reduce unnecessary noise and fuel burn without having to do a thing.

Ditch Witch has developed a technology that helps match power and speed to ground conditions. The RT70 tractor features a two-speed gearbox and three-speed on-the-fly shifting. To shift the mechanical gearbox, tractor motion must be stopped like normal. But then, to shift the hydraulic motor while the machine is still moving, the operator simply turns a knob that’s positioned to the left of the steering column.

“If you get into some tougher ground conditions and need to shift down to get a bit more power instead of speed, it’s easy to do without having to stop the machine and shift it,” Seabolt explains. “You can also shift up to take advantage of easier ground conditions.”

Those three on-the-fly speeds, in combination with the two-speed gearbox, give operators six possible speeds. In addition to the RT70, other larger Ditch Witch machines offer this same feature.

One innovation that is currently exclusive to the Ditch Witch RT70 is “crab and coordinated steering.” That won’t be for long, though, as Ditch Witch plans to incorporate it on other models over the next couple of years. This feature allows operators to turn the tractor with just the steering wheel, as opposed to needing a second lever to steer the rear axle separately.

“The traditional method of steering requires manual coordination and a bit of a learning curve,” Seabolt says. “Now operators just turn the steering wheel to make both axles do what they want depending on which mode the machine is in.

“In coordinated steering mode, the rear axle turns opposite of the front, allowing the operator to turn a tighter radius,” Seabolt continues. “The operator can also drive the machine in a ‘crab style’ where the front and rear axles are pointing in the same direction and the machine moves somewhat diagonally. Crab mode is beneficial when you’re plowing and want the machine to be closer to a fence line or building, or maybe hanging off the edge of a roadway when you’re driving on the roadway.”

Operator comfort

Trencher manufacturers have also been making design improvements to enhance operator comfort.

Ditch Witch’s RT70 tractor features a seat that swivels 120° (90° right, 30° left). “This allows the operator to position him or herself to ensure maximum visibility of the machine and work area,” Seabolt explains. At the same time, an informational display on the armrest shows all of the important operating parameters. Seabolt says an operator can glance at the display while looking back at the plow, helping him or her do the job better and more efficiently.

The 120° swivel seat is part of a broader effort by Ditch Witch to improve the overall operator station. Seabolt says it’s now a very open station with an enhanced line of sight to the rear and front of the machine, as well as the sides and tires when working close to curbs, buildings, or other obstacles.

A new centrifugal fan design has also improved operator comfort.

“With a traditional axial fan, you’re either pulling air in or pushing it across the cooler where it gets hotter and then across the engine where it gets even hotter,” Seabolt explains. “That hot air ultimately winds up near the operator. Our new centrifugal fan design pulls cool air in front of the machine and also into the back of the fan from the engine compartment. The air is then exhausted out both sides of the unit at a high velocity. The benefit is a much cooler workspace.”

To further cool the operator station, Ditch Witch has moved the hydraulic valves and pumps below the floorplate. “All that is in the operator’s environment now are electrical controls that don’t put off significant heat,” Seabolt points out.

Vermeer has focused on improving the layout of its operator controls. Since its operator station rotates to the right, all of the controls are now on the right. Vermeer has also taken steps to make its climate-controlled operator’s cab extremely quiet.

All of these technologies and design improvements are part of making productive trenching equipment that helps solve the pain points of today’s utility contractors — pain points that largely revolve around operator training, comfort, and productivity.

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Trenching through coral rock

We have a small project where we need to run conduit under a private street. The conditions are not very good. The asphalt has very little lime rock and under that is coral rock. I asked Sunbelt what they had, or if they had a rock saw. They have a ride on trencher like a Ditch Witch R100 but it’s located in Texas

Southeast Power

Due to the scarce nature of this machine, those of you that work in areas with dense rock, what method or machine do you use to cut through that type of material?

gpop

If you find a way tell us. We trench the easy then use a excavator with a rock bucket and another with a jack hammer. Around the lake we have rocks that are 1-3 feet thick but 20′ across. We just end up beating the hell out of them till they give.

MHElectric

How come every single job you guys do is a one-of-a-kind absolute crap show? Thats seriously impressive.

I’d think that sooner or later you would have a job where it wasn’t 2ft from the edge of the pool or digging a ditch across the lava crust on Mars.

Cow

No coral rock, but we have caliche over here.

Sometimes they use a jackhammer attachment on an excavator depending on how far they are going, other times they use a wheel trencher like you have posted for longer runs.

You can’t be the only contractor in your area dealing with the stuff, is there an excavation contractor you can sub, that’ll have the equipment to handle it?

Southeast Power

How come every single job you guys do is a one-of-a-kind absolute crap show? Thats seriously impressive.

I’d think that sooner or later you would have a job where it wasn’t 2ft from the edge of the pool or digging a ditch across the lava crust on Mars.

I really feel like Captain Quinn from the movie Jaws. Everyone turns down the job and they end up with us and have to pay the price. Lol

Southeast Power

No coral rock, but we have caliche over here.

Sometimes they use a jackhammer attachment on an excavator depending on how far they are going, other times they use a wheel trencher like you have posted for longer runs.

You can’t be the only contractor in your area dealing with the stuff, is there an excavation contractor you can sub, that’ll have the equipment to handle it?

micromind

When I lived in central Oregon, I’m pretty sure that the lava rock around there went all the way to China.

I would often use the DuPont Bro’s. Excavation Company. dynamite.

I don’t know how this would work in coral but in lava, a good-size dozer with a single ripper tooth on the back would cut a trench about 3″ wide and a couple of inches deep with each pass.

splatz

“You’re going to need a bigger ditch witch.”

That ditch witch might work or might fail misterably, that’s what we see around here, the rocks are way too big and way too hard.

Around here pretty much everyone with an excavator has a hydraulic hammer and don’t leave home without both. One utility company that was a customer of mine built a hydraulic hammer with a shaft like an old fashioned star bit. Your local ditchdiggers probably know how to handle it.

I wonder if that coral rock crumbles into coral sand, you might get lucky and it goes faster than you expect with the right machine. I don’t know if you hit it with a rotary hammer or anything to see just how hard it’s going to be.

US4542940A. Method and apparatus for cutting a trench through rock-like material. Google Patents

Publication number US4542940A US4542940A US06/103,231 US10323179A US4542940A US 4542940 A US4542940 A US 4542940A US 10323179 A US10323179 A US 10323179A US 4542940 A US4542940 A US 4542940A Authority US United States Prior art keywords boom traverse slots rock along Prior art date 1978-12-04 Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.) Expired. Lifetime Application number US06/103,231 Inventor Edward N. Marten Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.) HBZACHRY COMPANY H B ZACHRY Co Original Assignee H B ZACHRY Co Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.) 1978-12-04 Filing date 1979-12-13 Publication date 1985-09-24 1978-12-04 Priority claimed from US05/966,338 external-priority patent/US4230372A/en 1979-12-13 Application filed by H B ZACHRY Co filed Critical H B ZACHRY Co 1979-12-13 Priority to US06/103,231 priority Critical patent/US4542940A/en 1980-08-06 Assigned to H.B.ZACHRY COMPANY, reassignment H.B.ZACHRY COMPANY, ASSIGNMENT OF ASSIGNORS INTEREST. Assignors: MARTEN, EDWARD N. 1980-12-13 Priority to JP17645480A priority patent/JPS56128833A/en 1980-12-15 Priority to DE19803047176 priority patent/DE3047176A1/en 1980-12-15 Priority to CH921880A priority patent/CH645688A5/en 1980-12-15 Priority to IT50374/80A priority patent/IT1165572B/en 1980-12-15 Priority to FR8026577A priority patent/FR2472058B3/fr 1980-12-15 Priority to GB8040049A priority patent/GB2071182B/en 1983-08-15 Priority to GB08321921A priority patent/GB2136475B/en 1983-08-15 Priority to GB08321922A priority patent/GB2136476B/en 1984-05-25 Priority to US06/614,460 priority patent/US4662684A/en 1985-09-23 Priority to US06/779,148 priority patent/US4640551A/en 1985-09-24 Publication of US4542940A publication Critical patent/US4542940A/en 1985-09-24 Application granted granted Critical 2002-09-24 Anticipated expiration legal-status Critical Status Expired. Lifetime legal-status Critical Current

Images

Classifications

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F3/00 — Dredgers; Soil-shifting machines
E02F3/04 — Dredgers; Soil-shifting machines mechanically-driven
E02F3/18 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
E02F3/188 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with the axis being horizontal and transverse to the direction of travel

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F3/00 — Dredgers; Soil-shifting machines
E02F3/04 — Dredgers; Soil-shifting machines mechanically-driven
E02F3/18 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
E02F3/20 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels with tools that only loosen the material, i.e. mill-type wheels

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F3/00 — Dredgers; Soil-shifting machines
E02F3/04 — Dredgers; Soil-shifting machines mechanically-driven
E02F3/18 — Dredgers; Soil-shifting machines mechanically-driven with digging wheels turning round an axis, e.g. bucket-type wheels
E02F3/22 — Component parts
E02F3/24 — Digging wheels; Digging elements of wheels; Drives for wheels

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F3/00 — Dredgers; Soil-shifting machines
E02F3/04 — Dredgers; Soil-shifting machines mechanically-driven
E02F3/28 — Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets
E02F3/30 — Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom
E02F3/303 — Dredgers; Soil-shifting machines mechanically-driven with digging tools mounted on a dipper- or bucket-arm, i.e. there is either one arm or a pair of arms, e.g. dippers, buckets with a dipper-arm pivoted on a cantilever beam, i.e. boom with the dipper-arm or boom rotatable about its longitudinal axis

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F3/00 — Dredgers; Soil-shifting machines
E02F3/04 — Dredgers; Soil-shifting machines mechanically-driven
E02F3/96 — Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements
E02F3/961 — Dredgers; Soil-shifting machines mechanically-driven with arrangements for alternate or simultaneous use of different digging elements with several digging elements or tools mounted on one machine

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F5/00 — Dredgers or soil-shifting machines for special purposes
E02F5/02 — Dredgers or soil-shifting machines for special purposes for digging trenches or ditches
E02F5/08 — Dredgers or soil-shifting machines for special purposes for digging trenches or ditches with digging wheels turning round an axis

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F5/00 — Dredgers or soil-shifting machines for special purposes
E02F5/02 — Dredgers or soil-shifting machines for special purposes for digging trenches or ditches
E02F5/10 — Dredgers or soil-shifting machines for special purposes for digging trenches or ditches with arrangements for reinforcing trenches or ditches; with arrangements for making or assembling conduits or for laying conduits or cables
E02F5/104 — Dredgers or soil-shifting machines for special purposes for digging trenches or ditches with arrangements for reinforcing trenches or ditches; with arrangements for making or assembling conduits or for laying conduits or cables for burying conduits or cables in trenches under water

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F5/00 — Dredgers or soil-shifting machines for special purposes
E02F5/30 — Auxiliary apparatus, e.g. for thawing, cracking, blowing-up, or other preparatory treatment of the soil

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F9/00 — Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00. E02F7/00
E02F9/02 — Travelling-gear, e.g. associated with slewing gears
E02F9/024 — Travelling-gear, e.g. associated with slewing gears with laterally or vertically adjustable wheels or tracks

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F9/00 — Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00. E02F7/00
E02F9/08 — Superstructures; Supports for superstructures
E02F9/10 — Supports for movable superstructures mounted on travelling or walking gears or on other superstructures
E02F9/12 — Slewing or traversing gears

E — FIXED CONSTRUCTIONS
E02 — HYDRAULIC ENGINEERING; FOUNDATIONS; SOIL SHIFTING
E02F — DREDGING; SOIL-SHIFTING
E02F9/00 — Component parts of dredgers or soil-shifting machines, not restricted to one of the kinds covered by groups E02F3/00. E02F7/00
E02F9/28 — Small metalwork for digging elements, e.g. teeth scraper bits
E02F9/2866 — Small metalwork for digging elements, e.g. teeth scraper bits for rotating digging elements

Abstract

Apparatus and method for digging deep trenches having parallel generally vertical walls in solid rock such as limestone. The apparatus includes a transport means for providing support and for moving along a traverse on the earth’s surface while cutting a trench along that traverse. The transport carries a boom which may be articulated into the ditch being cut and a pair of rock cutterwheels carried on the end of the boom and assembled so that the outermost cutter teeth are wider than any other part of the boom assembly. The apparatus further includes means for aligning the flat surfaces of the rock cutter wheels parallel to and between the walls of the ditch and for maintaining alignment of the wheels with the trench as the transport moves along the traverse so that repeated cuts may be made to extend the trench to any desired depth. The trenching method includes the cutting of a pair of narrow slots by means of the rock saws as the transport moves along the traverse and then removing material between the slots. The method further includes repositioning the cutter wheels in a previously cut trench to make second cuts extending the depth of the trench to a preselected depth.

Description

This application is a continuation-in-part of my copending U.S. Pat. application Ser. No. 966,338, now U.S. Pat. No. 4,230,372 filed Dec. 4, 1978 which is thereby incorporated by reference.

This invention relates to apparatus and methods for digging trenches in the earth’s surface for laying pipes and the like, and more particularly to apparatus and methods for cutting narrow generally vertical walled trenches in solid rock such as limestone.

References which are known to the present applicant and which are believed to be relevant to the present invention include the following U.S. Pat. Nos.: 1,472,563 issued to Loken on Oct. 30, 1923; U.S. Pat. No. 2,780,452 issued to Marcerou on Feb. 5, 1957; U.S. Pat. No. 3,364,602 issued to Renzaglia on Jan. 23, 1968; and U.S. Pat. No. 428,951 issued to Richards on May 27, 1890; U.S. Pat. No. 2,517,267 issued to Watson on Aug. 1, 1950; and U.S. Pat. No. 3,596,997 issued to Valantin on Aug. 3, 1971.

The Loken patent discloses improvements to the bucket wheel trenching machines commonly used for pipe laying. Such machines are quite useful in most normal soils and even in some soft rocks, but the depth of cut is limited by the diameter of the bucket wheel itself. For very large depths, the equipment becomes quite massive.

The Marcerou patent teaches a rock cutting machine for use in quarries. The machine is manually adjustable and is designed to drive a pair of relatively small rock cutter wheels into the face of a stone wall while a head tool cuts a hole for the driving equipment and a pair of side cutters cut side grooves for stabilizing the device as it penetrates into the rock.

The Renzaglia patent teaches the use of a larger cutter wheel pivotally mounted on the back of a tractor for use in cutting roots. It is apparent from the illustrated apparatus that the depth of cut provided by this apparatus is limited to somewhat less than the radius of the cutter wheel.

The Richards, Watson and Valantin patents all teach mining machines having double rock cutter wheels or toothed chains for making multiple cuts into the face of a mine wall such as coal. None of these patents are adapted for digging trenches along a traverse on the earth’s surface since they are not adapted for cutting while moving and none of them provide sufficient articulation of the mechanisms to completely insert the cutter wheels into a previously cut trench and maintain alignment while the mechanism moves along a traverse.

Thus it is seen that while rock saws or cutter wheels have been known and used for various purposes, they have not been applied to the cutting of trenches for laying of pipelines. It can also be seen that it is desirable to provide a trench cutting apparatus capable of digging deep, narrow trenches in hard rocky materials which is relatively lightweight and simple compared to the prior known devices.

Accordingly, an object of the present invention is to provide a trench rock saw which can cut generally vertical walled narrow trenches to relatively great depth in solid rock materials.

Another object of the present invention is to provide a relatively simple and lightweight trenching machine capable of cutting trenches to relatively great depths.

Another object of the present invention is to provide an improved trenching machine and method of cutting trenches.

Trenching apparatus according to the present invention includes transport means for providing a support and for moving along a preselected traverse on the earth’s surface, a boom carried by the transport having a first end articulable into a substantially vertical walled trench in the earth’s surface along the traverse, a double rock cutter wheel assembly carried on the end of the boom, and alignment means in the transport and boom arrangement for aligning flat surfaces of the rock cutter wheels parallel to and in between walls of the trench being cut along the traverse and maintaining alignment so that the cutter wheels may be returned to the trench for subsequent cuts until a desired trench depth is reached. A method of digging trenches includes positioning of the dual rock cutter wheel assembly on and into the earth’s surface for cutting a pair of parallel vertically walled slots as the transport means moves along the preselected traverse and then removing material between the slots to provide a generally vertically walled open trench of a first depth. The method further includes repositioning the dual cutter wheel assembly in a previously cut trench and cutting vertically walled slots in the bottom of the open trench while the transport moves along the preselected traverse and again removing mateial between the slots to increase the depth of the vertically walled trench.

The present invention may be better understood by reading the following detailed description of the preferred embodiments with reference to the accompanying drawings, wherein:

FIG. 10 is a schematic illustration of a speed control unit adapted for use with the apparatus of FIGS. 8 and 9 and other embodiments of the present invention;

FIG. 13 illustrates an improved use of the apparatus of the present invention in cutting trenches beneath transverse pipelines.

With reference now to FIG. 1, most of the details of a first embodiment of the present invention are illustrated in a perspective view. A base 10 comprising steel I-beams assembled in a rectangle is supported on its four corners by traction units 12. Two of the I-beams forming base 10 also form a pair of tranverse rails 14 for supporting the rest of the apparatus. The remaining two I- beams 15 may also be used for cross rails in a slightly modified form of the present equipment. Arms 16 extend diagonally out from the corners of base 10 and connect the traction units 12 to the base. A pivot 18 is provided at the end of each arm 16 to allow the traction units 12 to move in essentially any direction and also to allow the arms 16 to be raised relative to traction units 12. It can be seen that since base 10 and arms 16 form a rigid, flat surface and the surface of the earth is rarely perfectly flat, especially in construction areas, it is necessary that at least some of the arms 16 have the capacity for being raised relative to the traction units 12. While, as illustrated, each of the traction units 12 is independently free to rotate about its pivot 18, it is normally desirable to provide lateral tie rods to keep pairs of the traction units 12 aligned with each other. In this embodiment each of the traction units 12 is a conventional crawler unit riding on steel treads and driven by a fluid- drive motor 20 through a gear reducer 21. For general use, the treads of traction units 12 are not cleated, making it more important that the extension arms 16 have the ability to be raised relative to the traction units 12 to assure even loading of each of the units 12.

Four rollers or wheels 22 are provided for riding in the rails 14 and, in turn, suporting a turntable 24. The rails 14 and rollers 22 provide, in this embodiment, means for moving the rest of the apparatus of FIG. 1 laterally relative to the base. The turntable 24 is conventional and is driven by a fluid-drive motor 25 to provide rotational motion to the unit about a vertical axis 26. A second frame 28 is supported on turntable 24 to pivot around axis 26.

Supported on frame 28 is a prime mover 30 which in this embodiment is a diesel engine. The engine 30 drives a pair of hydraulic fluid pumps 32 for driving the traction motors 20 and the cutter head motor described below. The engine also drives another pump 34 for operating the numerous hydraulic cylinders which position the various elements of the present apparatus. A pair of hydraulic fluid tanks 36 provide the storage capacity for the hydraulic fluid used to operate the motors and cylinders.

The second basic unit supported by frame 28 is an extendable boom unit 38. In this embodiment, unit 38 is a unit commonly used for truck mounted backhoes and the like. The unit 38 is attached to frame 28 by means of a pivot axle 40 and the pivot angle is controlled by a pair of hydraulic cylinders 42. The boom portion 44 of unit 38 is rotatable about its longitudinal axis by means of a ring gear arrangement 46. An extendable portion 48 of boom 44 telescopes from within boom 44 to provide a variable extendable length. Each of the various motions of boom unit 38 is hydraulically controlled and powered from the prime mover 30. It can be seen from the arrangement so far described that the extendable boom portion 48 may, with respect to the base 10, translate laterally, rotate about a vertical axis, pivot about a horizontal axis, rotate about its own longitudinal axis, and extend along it longitudinal axis. These motions are, of course, additive to the basic motion of frame 10 which is able to translate by means of traction means 12 in essentially any direction on the surface of the earth.

Attached to the end of extendable boom 48 is a dual cutter unit shown generally as 50. Cutter unit 50 is attached to boom 48 by pivot 52 and a hydraulic cylinder shaft 54. The dual cutter 50 comprises a main body 56 containing reduction gearing within it and supporting a fluid- drive motor 58 and a pair of cutter wheels 60. Motor 58 drives directly into a gear reduction unit 62. The reduction unit 62 in turn drives a double chain drive speed reduction arrangement shown in more detail in FIG. 2. The two cutter wheels 60 are eight feet in diameter (seven feet without carbide teeth) and the teeth are spread over a five inch width. The cutter wheels are designed to rotate up to 105 revolutions per minute. The cutter wheels 60 are mounted on opposite ends of a shaft 64 which has an overall length less than the maximum spread between the outer teeth on the cutter wheels. The details of this arrangement are better illustrated with respect to FIG. 2.

With reference now to FIG. 2, a front view of the apparatus in FIG. 1 is illustrated in place cutting a deep trench in a rocky material. The same designation numbers are used to indicate the parts which are also illustrated in FIG. 1. In particular, the traction units 12 are shown resting on the top of banks 66 comprising loose or soft surface topsoil or sand. Below an interface 68 is a subsurface rocky material such as a limestone material. While limestone is relatively soft stone and could sometimes be cut by previously known trenching equipment, such cutting could be done only at a slow rate and would cause extreme wear on the equipment. The cutter wheels 60 have teeth 70 designed for cutting this type of rocky material at a fairly high rate, but equipment for using such cutter wheels has not heretofore been provided which could cut a trench deeper than about the radius of the cutter wheel. As noted above, the shaft 64 is shorter than the space between outside teeth 70 of cutter wheels 60 which in this embodiment is about thirty inches. Likewise, the housing 56 in which the driving mechanism is contained and even the extendable boom 48 and boom 44 are smaller than this thirty inch dimension so that the entire boom and drive mechanism may be extended down into a previously cut thirty inch wide trench. As illustrated in FIG. 2, an essentially vertical walled trench 72 has been cut ino the solid rock portion of the earth below the loose material 66. As illustrated, trench 72 was about eight feet deep when dual cutter 50 was inserted to make another cut at the bottom. The cutter 50 provides a pair of narrow slots 74 approximately three feet deep and each five inches wide with the outer edges of the cuts being approximately thirty inches apart. It can be seen that it is very important in this operation that the large cutter wheels 60 are correctly positioned within the previously cut trench 72 so that the contact of teeth 70 is limited to the bottom of the trench where the desired cut is to be made. Any misalignment of the cutters 60 would cause them to bite into the side walls of the trench greatly increasing the force needed to drive the wheels 60 and either stopping the cutting operation or damaging the wheels or the equipment.

In operation, a trench is cut in hard rock by first removing the soft topsoil layer to form banks 66 by use of conventional earth moving equipment. When the hard rock interface 68 is reached, the trench rock cutter according to the present invention is positioned over the topsoil cut 66 as shown in FIG. 2. The frame 28 is then positioned over the center of the cut by movement along rails 14 by hydraulic cylinders means not shown. The boom unit 38 is then rotated about vertical axis 26, tilted about pivot axis 40 and the boom is extended and rotated until the cutter wheels 60 contact the top surface of the rock formation. Before cutting begins, the wheels are carefully aligned to be parallel with the direction of the desired cut. The cutter wheels are then rotated and lowered into the rock face until they reach the maximum depth of about three feet. The entire unit may then be translated down the trench by means of traction units 12 as the parallel grooves 74 are cut into the rock face. As the entire unit moves, the boom unit 38 may be continually readjusted to ensure the parallel operation of the blades with respect to the direction of the desired cut. After the parallel cuts 74 have been made, conventional means such as backhoes, side chisels, or explosives are used to remove a central block portion 76 remaining between the two side cuts. It can be seen that once the side cuts 74 are made, the central portion 76 is much more easily removed than would be otherwise possible. After the first pass has been made and the central portion 76 has been removed, the rock cutter of this embodiment may be returned to the starting point and repositioned. The essentially universal articulation of the boom unit 38 is then employed to lower the cutter blades 60 into the previously cut trench with essentially no contact with the sides walls of the trench. In this way, the cutter blades may be lowered into the bottom of the previously cut trench to provide another pair of narrow grooves along the length of the trench. The remaining rock 76 is again removed by conventional means and the process may be repeated until a desired depth is reached. With the fairly simple apparatus of the present invention, total trench depths of approximately twenty-seven feet may be provided. It can be seen that with very little additional increase in size and weight of the equipment, the total cut depth may be increased by simply providing a longer boom arrangement 44.

As noted above, the base 10 is rectangular with the two rails 14 comprising the long sides of the rectangle. The remaining short sides 15 may also be used as rails for supporting the apparatus by wheels 22. Thus, if it is desired to operate with smaller spacing between traction units 12, the base 10 may be rotated 90° relative to wheels 22 with an appropriate change in wheel 22 spacing. The traction means 12 would then also be pivoted 90° on pivot units 18 and the entire unit would operate as described above, but with narrowed spacing between traction units 12. In the preferred embodiment, the base 10 is about seven by ten and one half feet. As an alternative, the connection between traction support arms 16 and the base 10 may be made flexible to allow the space between traction units 12 to be varied.

As noted above, traction unit pivots 18 are provided with means for raising base 10 relative to the units 12. This is shown as shaft 78 in FIG. 2. Not only does this improve traction, but it also allows base 10 to be levelled, which greatly facilitates alignment of cutter wheels 60 with a previously cut trench. But it can be seen that even if the base 10 is tilted with respect to the verticle, the articulation which is otherwise provided is sufficient to perfectly align the cutter wheels 60 within a previously cut trench.

The apparatus thus far described is adapted for cutting only a single width of trench, i.e. thirty inches. A simple means has been found for increasing the width of the cut. While shaft 64 could obviously be modified to have a length greater than thirty inches, it has been found more convenient to use hub extensions between the ends of shaft 64 and cutter wheels 60. Up to three, six inch extensions may be used on each end of shaft 64 to provide a trench width of up to sixty-six inches. While wider trenches provide more clearance for boom 44, the universal articulation of the cutter mechanism is still required to properly reenter a trench.

While many are not illustrated, for simplicity, it is apparent that fluid-driven cylinders, etc., are used to control the various allowable motions of the apparatus of FIGS. 1 and 2. Each of the fluid-driving means derives power from the prime mover 30.

Experience with use of the embodiment of the present invention illustrated in FIGS. 1 and 2 has shown that smaller embodiments of the present invention may be used to great advantage. In FIGS. 1 and 2 the apparatus is large enough to span a fairly broad ditch formed in loose material 66 by conventional equipment. In practice, it has been found much better to remove the topsoil layer above the interface 68 by use of the dual rock cutter apparatus of the present invention rather than more conventional apparatus. Cutting through even relatively unconsolidated topsoil with the apparatus of the present invention does very little to disturb the adjacent materials and in most cases a stable ditch wall can be formed even in the topsoil layer. As a result, it is not necessary to provide as much space between the traction means as was originally thought and as was provided in the FIG. 1 embodiment. It has also been found that with experience, an operator of the equipment can maintain the transport mechanism in very close alignment with a preselected traverse, including a previously cut trench. As a result, it has been found that only a small degree of lateral motion need be provided to the boom to allow repositioning of the cutter wheels in a previously cut trench. That is, while universal articulation is still required in most cases, the range of motion need not be as great as was first thought. As a result of the experiences with the FIG. 1 embodiment, various other embodiments, some of which are considerably smaller, have been developed and are described below.

With reference now to FIG. 3, second embodiment of the present invention is illustrated in perspective view. A transport means 78 for this embodiment is supported on a pair of crawler type traction means 80 and carries a diesel engine 82 for providing all power for the unit. This type of transport is commonly used for supporting conventional drilling equipment. The engine 82 drives a number of hydraulic pumps for powering both the tracks 80 and the trench cutting equipment carried on the transport. A pair of small constant output hydraulic pumps 84 are provided for driving numerous hydraulic cylinders which control positioning of the cutter blades as described below. A variable displacement hydraulic pump 86 is provided for driving the cutter blades at a variable and controllable rate. Two other variable displacement hydraulic pumps 88 are provided for driving the traction means 80 to also provide variable speed and steering. The hydraulic outputs from pumps 88 are coupled to a pair of hydraulic motors (not shown) which in turn drive the threads 80. This variable displacement hydraulic pump arrangement gives the operator a wide range of operating speeds and also allows automatic control as explained below with respect to other embodiments.

An extendable boom 92 which may be identical to the extendable boom 38 of FIGS. 1 and 2 is carried on the transport means 78. The coupling of the boom 92 to the base 78, as will be seen, provides essentially all of the motions provided in the FIG. 1 embodiment but with several of the motions limited to a narrower range of operation. In particular, there is provided on a front cross-beam 94 of the transport 78 a pivot point 96. A partial turntable 98 is supported upon pivot 96 for rotation about a vertical axis. A number of restraining guides 100 are provided on the forward cross beam 94 and an intermediate cross-beam 102 of the transport 78 for holding the plate 98 down while allowing limited rotation of the plate. In particular, in the present invention, the plate 98 is allowed to rotate a total of from 15° to 20° about the pivot point 96. With this limited motion, a simply hydraulic cylinder connected between plate 98 and either of the cross-beams 94 or 102 is quite sufficient for controlling the position of turntable 98.

The boom 92 is supported on the turntable 98 by what can be considered a universal joint connection. A longitudinal pivot axis is defined by a pair of pivot pins 104 carried on the front and back edges of turntable 98. A boom support member 106 is pivotally carried by the pivot pins 104 and thereby allowed to tilt or pivot to the left and right with respect to the longitudinal axis of the transport 78. A pair of hydraulic cylinders 108 are connected between the support element 106 and turntable 98 to control this left-right lateral movement of the boom 92. Another pair of pivot pins 110 connect the boom 92 to the support member 106 for providing pivoting of the boom 92 about a transverse axis relative to the transport 78. Another pair of hydraulic cylinders 112 is connected between the turntable 98 and the boom 92 to control the pivoting of the boom about pivot points 110.

This arrangement for supporting boom 92 on transport 78 provides limited rotation of the boom about a vertical axis and limited left-right translation of the boom by means of the pivots 104. In this embodiment, the left-right motion of boom 92 is limited to nine inches to the left and twelve inches to the right when facing the boom end of the machine with the difference being due to the fact that the operator’s cab is normally positioned on the left side and interferes with further motion of the boom in that direction. It is apparent that lateral movement of boom 92 by pivoting also tends to pivot the cutter blades on the end of the boom which would cause misalignment of the blades in a previously cut trench. However, as with the FIG. 1 embodiment, the boom 92 includes a rotary bearing arrangement 114 which allows rotation of the extended portion of boom 92 about its own longitudinal axis. With only very limited use of this rotary bearing 114 any tilting caused by pivoting about pivot points 104 as well as any tilting caused by an uneven ground surface is easily compensated for.

In this FIG. 3 embodiment a cutter head attachment 116, which may be identical to that illustrated in FIGS. 1 and 2, is carried on the end of boom 92 and may be used in the same manner as described above. In this embodiment the rock cutter blades are essentially identical to those used in the FIG. 1 embodiment but have an outer diameter of 6.5 feet. In addition to hydraulic cylinder means 120 coupled between the boom 92 and the cutter head 116 for controlling relative position, an adjustable locking link 122 is also provided. Each cut made by the blades 118 is made at a relatively constant depth and it is usually desirable for the head 116 to be at a constant angle during the cutting process. Therefore the angle between the head 116 and boom 92 needs to be changed only when a new cut is started at a new depth. At such time the cylinder 120 may be used to readjust the head 116 relative to boom 92 and the link 122 is then fixed by pins 124 to maintain the constant relative angle.

With the features illustrated in FIG. 3 and thus far described, it can be seen that this FIG. 3 embodiment may be used in essentially the same manner as the FIG. 1 embodiment. That is, the transport 78 may be positioned over a preselected traverse on the earth’s surface and moved along that traverse while the cutter blades 118 are used to cut a pair of slots having essentially vertical walls along that traverse. The depth of the cutting is controlled by pivoting the boom 92 about pivot points 110 under control of cylinders 112. Vertical alignment of cutter blades 118 can be controlled by rotating boom 90 by means of the rotary bearing 114. Should the transport 78 turn so that it is not parallel to the desired traverse, the entire cutter mechanism may be pivoted about the vertical pivot point 96 to maintain alignment with the desired traverse. Likewise if the transport 78 should be laterally displaced relative to the traverse, the boom 92 may be pivoted about the longitudinal pivot points 104 and thereby moved laterally so that alignment of boom 92 with the traverse is maintained. It will become apparent that the primary mechanism for aligning the boom 92 with the preselected traverse is in fact the transport means 78. The operator of the mechanism uses differential control of the speed of traction means 80 by controlling the output of the hydraulic pumps 88 to “drive” the transport 78 along the desired traverse. As is well known in the control of dual track transport mechanisms the mechanism actually tends to follow a somewhat zigzag course as the operator makes corrections to maintain alignment with the preselected traverse. That is, to move to the operator’s right, the left track must be speeded up to rotate the transport 78 slightly out of alignment with the traverse so that its motion will carry it to the right and back into correct transverse position. Once at that correct transverse position, the operator must then speed up the right track to rotate the transport 78 back into correct alignment with the traverse. A skilled operator can maintain the transport 78 parallel with a preselected traverse and in proper transverse position relative thereto within fairly close limits. It is for this reason that the boom 92 is coupled to the transport 78 with universal articulating mechanisms which have only limited maximum motions but which are sufficient to maintain perfect alignment of the boom 92 as the transport 78 is driven.

A very simple, yet very effective, aid to the operator of the transport 78 is a simple string line alignment guide. In one form, this comprises a simple arm 126 extending transversely from the frame of the transport 78 and carrying a string or chain supported pointer or plumb bob 128. A string line may be laid out at a selected lateral position relative to a surveyed traverse and the lateral position of plumb bob 128 relative to the center line of transport 78 is accordingly adjusted. By positioning the alignment guide on the end of the transport 78 opposite from cutter wheels 118, the operator can quickly detect misalignment of transport 78 with the desired traverse. He can then make the slight adjustments required in the speed of tracks 80 to maintain the appropriate alignment.

Several other important features of the present invention are illustrated in FIG. 3 and in FIG. 4 which is a side view of the cutter head 116 and wheels 118 cutting a trench. It has been found desirable in most cases to provide fenders 130 spaced from the periphery of cutter wheels 118 to deflect cuttings back into the slots cut by the wheels. The fenders 130 aid in keeping down dust generated in the cutting process. Additional dust suppression is achieved by use of a fine mist water spray directed towards the cutter wheels 118. A hose and pipe condiut 132 carried by boom 92 and the head 116 conducts water to the location of the fenders 130. A pair of nozzles 134 are carried below the fenders 130 and directed towards cutter wheels 118. The water spray arrangement was initially intended to only keep down dust generated in the process. It has also been found very effective at cooling the cutter blades 118 and thereby greatly extending the life of the blades. A third advantage of the water spray which was not anticipated is consolidation of trench walls. As noted above, cutting trenches in the near surface or topsoil layers with the present apparatus does not disturb adjoining topsoil and vertically walled trenches usually result so that the total amount of material removed is greatly reduced. The water spray has been found to aid in consolidating these otherwise soft walls and reducing the chance of collapse or cave-in of the topsoil portions of the trench walls.

A final feature illustrated in FIGS. 3 and 4 is an arrangement for laying explosive cord in the bottom of slots cut by the wheels 118. This arrangment includes reels 136 of explosive cord carried on the cutter head 116, a tubular guide 138 supported on fenders 130 and a plow, or crumbing shoe, 140 carried on the end of guide 138. The guide 138 closely follows the periphery of the wheel 118 to the bottom of a trench cut by the wheel. The guide 138 then extends along the backside of plow 140 to the bottom portion of a slot cut by the wheel while the plow 140 curves back under the wheel 118 to push loose cuttings back into the path of the wheel.

FIG. 4 most clearly shows the details of this explosive cord laying process. Thus, in FIG. 4 it can be seen that cuttings removed from the trench at point 142 are carried up under the fender 130 and directed by the fender back down along the backside of cutter wheel 118 and thereby back into the slot 144 cut by the blade 118. It is desireable for the explosvie cord 146 to be positioned at the very bottom of the slot 144 for best results. It is also desireable for the slot 144 to be totally filled with cuttings above explosive cord 146 before detonation. It has been found that a majority of the cuttings tend to be thrown behind the wheel 118 by sufficient distance to fall above the explosive cord 146. Some of the cuttings however, tend to fall directly behind the blade 118 and tend to be positioned under explosive cord 146. The plow 140 closely follows the outline of cutter wheel 118 and pushes the cuttings in the slot 144 back into the path of blade 118 so that they are carried around the wheel for deposit behind the wheel a second time. This arrangement effectively provides a clear path for laying explosive cord 146 at the bottom of trench 144.

Trenches are cut with the apparatus of FIGS. 3 and 4 in the manner described with respect to FIG. 1. After the pair of vertical slots are cut by the cutter wheels 118 and the explosive cord has been laid in the bottom of the slots and tamped with cuttings deposited over the explosive cord, the mechanism can be removed from the trench momentarily while the explosive cord is detonated. This arrangement very effectively shatters the rock material between the slots 144 leaving a trench filled with rubble. This rubble is easily removed by a conventional backhoe having a clean vertically walled trench. This process is repeated to achieve greater depth as described above with respect to the FIG. 1 embodiment.

With reference now to FIGS. 5 and 6, there are provided top and side views of a third embodiment of the present invention in which a conventional bulldozer is modified and used as the transport means. The bulldoze 150 is, in this embodiment, a Fiat Allis 41-B 540 horespower tractor. Traction means therefore comprises a conventional pair of tractor threads 152. As shown in the broken away portions of the drawings, the tractor 150 has been modified to provide low speed motion required for the present invention. In particular, the conventional drive shaft connecting a torque converter 154 driven by the engine to a transmission 156 has ben removed. A gearbox 158 and at least three hydraulic pumps 160 have been coupled to the output of the torque converter 154. The hydraulic pumps provide fluid for driving the treads 152, the cutter wheels and the hydraulic cylinder actuators required for positioning the various portions of the apparatus. A hydraulic motor 162 is connected to a conventional drive shaft 164 normally used as a power take off from transmission 156. The motor 162 is driven by one of the hydraulic pumps 160 and provides low speed drive to transmission 156 which in turn drives the treads 152 in an otherwise conventional manner. These modifications were made since it is important in the present invention that the transport means, in this case tractor 150, move at a controlled constant rate while the rock cutter blades are cutting slots along the traverse. This type of tractor normally would not provide the desired motion at the required low speeds.

A boom 166 is carried from the rear of tractor 150 and supports a rock cutter head 168. In this embodiment, the boom 166 is connected to tractor 150 by a universal motion element 170. The element 170 is connected to the tractor 150 by two horizontally spaced pivot points 172 to provide rotation about a horizontal axis transverse to the center line of tractor 150. A pair of hydraulic cylinders 174 provide the means for controlling the position of element 170 about the pivot 172. The boom 166 is connected to the element 170 by a pair of vertically spaced pivot points 176 which allow the boom 166 to pivot about a vertical axis located near the rear of tractor 150. A hydraulic cylinder 178 controls the pivoting of boom 166 about this vertical axis. The cutter head 168 in this embodiment is an improved twin-blade rock saw attachment, details of which are illustrated in FIG. 7 and described below. The cutter head 168 is attached to the end of boom 166 by a locking link 180 essentally indentical to the link 122 in FIG. 3. Link 180 is again adjusted for a particular cut to provide a desired angle between cutting head 168 and boom 166. The cutting head 168 should remain either generally horizontal or generally vertical during the cutting of a particular trench depending upon the methods being used to cut a particular trench. In addition, cutter head 168 includes a rotary joint 182 which allows the main portion of the head 168 to be pivoted relative to a plate 184 which is connected to the boom 166. The details of this arrangement are better illustrated in FIG. 7.

In use it can be seen that the boom 166 may be pivoted right or left and up or down relative to the rear of tractor 150. In addition the cutter head 168, if in a vertical position, may be pivoted about a vertical axis for alignment of cutter blades 186 with a desired traverse. Therefore, for conventional cutting, the cutter head 168 is positioned generally vertically. The tractor operator then aligns the tractor 150 with the desired traverse with the treads straddling the trench location. It is desireable for the operator to have a string line guidance arrangement as shown in FIGS. 3 and 4 but he may use the edge of the blade 188 on the front of tractor 150 as his position indicator if desired. The operator then uses the hydraulic cylinder actuaters 174 and 178 to position the boom so that the cutter head 168 is positioned precisely above the desired trench location. If the tractor is not perfectly aligned parallel to and centered over the surveyed traverse, the cutter blades 186 will tend to be misaligned with the traverse and the rotary joint 182 is used to make a correction. The cutter blades 186 are then driven from one of the hydraulic pumps and lowered into the surface to begin cutting the trench. The driver then begins moving the tractor 150 along the traverse attempting to maintain precise alignment. As in the embodiment of FIG. 3, the driver’s course corrections will pivot the tractor 150 out of alignment with the traverse. As this occurs, the boom 166 may be pivoted left or right as necessary to maintain the cutting head 168 precisely over the traverse. Angular errors of the blades 186 are then corrected by rotation of the cutter head at rotary joint 182. This articulation is sufficient therefore to correct for both lateral and angular displacements of the transport 150 relative to the desired traverse.

In some cases it will be desireable when cutting fairly shallow trenches requiring only one or two passes of the trench cutter to position the cutter head 186 in alignment with boom 166, that is generally horizontal. Thus, if a shallow ditch needs to be cut and the surface of the earth is unlevel, it is still desireable for the trench walls to be essentially vertical. In such a case, the rotary joint 182 can be used to maintain the cutter blades 186 vertical even when the tractor is leaning to the right or left due to the unlevel surface.

The embodiment shown in FIGS. 5 and 6 is generally intended for cutting shallower trenches than could be provided by the FIGS. 1 and 3 embodiments. The depth of trenches in this embodiment can however be increased by adding extensions between the end of boom 166 and the cutter head 168 itself. Since cutter head 168 is hydraulically driven there is no particular difficulty in providing such extensions. The arrangement as illustrated is intended for cutting to a depth of about nine feet and heavier equipment would normally be used for cutting deeper trenches.

Although not illustrated in this embodiment to simplify the drawing, it is desireable to include the water spray and explosive cord placement apparatus which was illustrated in FIGS. 3 and 4. With this additional apparatus, the embodiment of FIGS. 5 and 6 is used in essentially the same manner as discussed above. The only difference is that since lateral displacement is achieved by pivoting about a vertical axis at the back of tractor 150 it is necessary to provide the rotary joint in the cutter head 168.

With reference now to FIG. 7 there is provided a cross-sectional illustration of the cutter head 168 of FIGS. 5 and 6 taken along the line 77 FIG. 6. The new head 168 is less complicated than the cutter head 50 of FIGS. 1 and 2 and provides a cleaner exterior shape for positioning within trenches. In particular, this head 168 comprises a generally rectangular housing 190 having only two rotating axles 192 and 194 carried therein. The axle 192 carries the rock cutter wheels 186 in essentially the same way as provided in the FIG. 1 embodiment. The other shaft 194 is connected directly to the output of a hydraulic motor 196 carried completely within the housing 190. In this embodiment the motor 196 is sold under the Tradename and part number of Hagglund 4160 Hydraulic Motor. The only portions of the motor external of housing 190 are inlet conduits 198 provided for connection to flexible hydraulic hoses. The rotating shafts 192 and 194 are coupled together by a plurality of sprocket wheels 200 and 202 carried on shafts 192 and 194 respectively and coupled together by a chain 204. Due to the simple construction, this cutter head is believed to be preferable to that shown in FIGS. 1 and 2.

At an end of housing 190 opposite the cutter wheels 186, there is formed an end plate 206. The rotary joint 182 of FIGS. 5 and 6 is supported on this end plate 206. The plate 184 is also supported by the rotary bearing 182 and is the plate to which the boom 166 of FIGS. 5 and 6 is connected. Extension booms may also be connected to plate 184 if desired. In this preferred embodiment a hydraulic cylinder 208 (FIG. 6) is connected between the end plate 206 and the plate 184 to provide means for rotating the housing 198 relative to the plate 184. Only limited relative motion is required and the hydraulic cylinder arrangement is generally sufficient for this purpose. It is of course apparent that if greater extent of relative rotation was required that ring gears and rotary hydraulic motors could be employed for the purpose.

With reference now to FIGS. 8 and 9, there are provided top and side views of a fourth embodiment of the present invention. In this embodiment a transport mechanism 210 comprises a conventional tracked backhoe having a pair of crawler treads 212. The conventional mechanism also includes an engine 214 and a boom 216 both supported upon a turntable 218 carried by the tracks 212. The boom 216 may be raised or lowered about a horizontal pivot point 220 by means of hydraulic cylinders 222. Boom 216 is designed for carrying a bucket or scoop on its extended end and includes a hydraulic cylinder 224 fo controlling motion of that scoop, although the scoop is not used in this embodiment. In this embodiment, the rock cutter head 226, which is perferrably identical to that illustrated in FIGS. 5, 6, and 7 is supported on the end of boom 216 with its position controlled by cylinder 224. The cutter head 226 does preferrably include the rotary joint 228 in this embodiment.

As with other embodiments, the basic transport mechanism 210 has been heavily modified for use as a dual rock cutter trencher according to the present invention. An engine and hydraulic pump module 230 has been attached to the rear of the engine compartment 214 of the basic transport mechanism. This module includes another diesel engine 232 which drives a number of hydraulic pumps. A first variable displacement hydraulic pump 234 is connected to engine 232 to provide a variable speed drive to the cutter wheels in cutter head 226. Additionally a pair of variable displacement hydraulic pumps 236 are driven by engine 232 to provide power to the traction treads 212. The basic transport 210 employed hydraulic drives for the treads 212 but in the preferred embodiment these have been replaced with hydraulic motors which can provide slower speed operation. Each of the hydraulic motors is individually driven by one of the pumps 236 so that the speed of each traction means 212 may be very accurately and individually controlled. The remaining hydraulic cylinders and other actuators, such as the motor which controls the position of turntable 218, are driven by the original engine and hydraulic pump set 214 forming part of the basic transport mechanism 210.

In use, the embodiment of FIGS. 7 and 8 is again able to position rock cutter head 226 so that cutter blades 238 are accurately positioned along a desired traverse on the earth’s surface. As with the other dual track transports the basic means for maintaining alignment with the traverse is the transport 210 itself. In this case, the boom 216 may pivot about a vertical axis by means of turntable 218 and may pivot about the horizontal axis 220. With these motions the extended end of boom 216 can be maintained along the appropriate traverse even when the traction means 210 is not in precise alignment. As with earlier embodiments, the rotary joint 228 allows the head 216 to remain perfectly parallel to the traverse even when the traction means 210 is misaligned.

As with the FIGS. 5 and 6 embodiment, the cutter head 226 may be positioned either vertically as shown in FIG. 9 or may be extended essentially horizontal from boom 216. In the vertical position as illustrated rotary joint 228 provides alignment as discussed above. In addition, this embodiment allows the cutting of trenches immediately adjacent an obstruction such as a building which abuts a right-of-way. That is the boom 216 may be pivoted by means of turntable 218 so that the cutter head 226 lies to the side of one of the treads 212. With the cutter head 226 vertical, the blades may then be rotated to be parallel to the desired traverse as the transport 210 moves along parallel but laterally displaced from the traverse. Again, it is desireable in all cases to provide some guide arrangment such as a string line so that the operator may maintain the treads 212 parallel to the traverse and at a preselected lateral displacement therefrom. It can be seen in this offset trenching arrangement that the bottom 216 could not be extended into previously cut trenches to any great extent. To increase the trench depth, an extension boom may be connected between the cutter head 226 and the boom 216 as discussed above.

If it is desired to cut a vertical walled trench in a sloping ground surface, the cutter head 226 may be positioned horizontally. If the traction means 212 are then uniformly spaced about the desired traverse and boom 216 is used to lower the mechanism into a trench the rotary joint 228 may be used to maintain the cutter wheels 238 in the vertical position.

With reference now to FIG. 10, there is illustrated a diagram of a speed control system found particularly useful with the present invention. As noted above, cutting of the slots forming the trenches in the present invention occurs primarily as the transport mechanism moves along the preselected traverse. The speed of cutting is therefore related to the speed of motion. It is of course clear that there are maximum limits to the cutting rate beyond which excessive power would be required and the cutter wheels would be damaged. On the other hand, it is apparent that if the transport mechanism moves too slowly the equipment will be operating below capacity, that is, inefficiently. In FIG. 10 an engine 232 and pumps 234 and 236 are the same as those shown in FIGS. 8 and 9. Pump 234 drives a hydraulic motor 240 having an output shaft 242 which drives the cutter wheels 238. Likewise a hydraulic motor 244 has an output shaft 246 for driving one or more crawler treads. A hydraulic fluid line 248 supplies hydraulic fluid from pump 234 to the cutter motor 240 at a rate controlled by a manual control device 250. As the motor 240 speed is increased manually by increasing the output of pump 234 the pressure in line 248 increases. In addition, as the resistance to rotation of the cutter wheels 238 increases, the pressure in line 248 also increases. A pressure detector 252 is coupled to line 248 and provides an output to an indicator dial 254. For automatic control, detector 252 also provides an output to an automatic speed control unit 256 which in turn provides an output coupled to the hydraulic pump 236. The speed control unit 256 causes the output of pump 236 to increase in response to a decrease of pressure in line 248 and likewise causes the output of pump 236 to decrease in response to an increase in the line 248. That is, as a resistance to cutting by wheel 238 decreases the drive motor speed is increased to move the transport 210 along the traverse more quickly which will in turn increase the resistance to cutting felt by the blades 238. In this way the unit may be run at a high output power level without fear of exceeding the limitations of the equipment. If, for instance, an excessively hard section of rock should be encountered, the resistance of cutting will increase and the speed control of 256 will automatically slow the transport mechanism and thereby avoid overloading the cutter wheels 238. The pressure indicator 254 is positioned where the operator of the mechanism can monitor the cutter motor pressure and make adjustments in the speed control mechanism 256 to increase or decrease the operating pressures. In general, the operator need only use the manual control 250 to control the output of pump 234 to thereby control the power supplied to the cutter wheels and the speed of the transport 210 will be automatically adjusted accordingly.

DM Civil’s Tesmec TRS 1475 Trenching Rock Saw

Great increases in cutting efficiency have been achieved without an automatic speed control system merely by use of the pressure detector 252 and indicator 254. The operator of the system sets the manual control 250 to a predetermined cutter motor speed and then manually controls the output of the drive motor pump 236 while observing the pressure supplied to the cutter motor 240. That is, as the cutter head pressure increases the operator slows the transport to avoid overloading the cutter wheels. The automatic system is preferred to relieve the operator of the constant observance of the pressure indicator 254. It is apparent that the FIG. 10 diagram is somewhat simplified since for directional control of the transport 210 a pair of the pumps 236 and motors 244 must be provided. The operator steers the transport by adjusting the relative speeds of the two drive motors which can be done by simply adding control signals modulating those supplied from speed control 256 to the variable displacement pumps 236. It is also apparent that this hydraulic speed control by reference to cutter head motor pressure is useful and preferred in essentially all embodiments of the present invention.

With reference now to FIGS. 11 and 12 there are provided top and side views of yet another embodiment of the present invention. Generally stated, this embodiment is a barge mounted trencher for use in cutting generally vertically walled trenches in the floor of a body of water. A barge 260 is provided having a central opening 262 extending through to the water. The barge 260 may be formed from eight modular barge units designed for assembly into barges of various shapes and sizes with a central module omitted to provide the opening 262. A boom 264 which may be identical to the boom 216 of FIGS. 8 and 9 is carried on a forward end 266 of the opening 262. The boom 264 may be raised or lowered by means of hydraulic cylinders 268 in a conventional manner. A cutter head 270 preferrably identical to that illustrated in FIGS. 7, 8 and 9 is suspended from the end of boom 264 in the same manner as previously illustrated and described. The attachment of boom 264 to wall 266 also preferrably allows some lateral translation of the boom 264 relative to the barge 260. For this purpose, pivots 272 support the boom 264 and are carried on transverse rails and a hydraulic cylinder (not shown) is provided for positioning the boom 264 laterally along the rails.

A conventional backhoe unit 274 is preferrably supported on an aft end 275 of barge 260 for clearing trenches cut by the cutter head 270. The backhoe 274 is preferrably mounted on a turntable so that rubble may be lifted and moved to the side of the desired traverse.

A power pack 276 similar to the unit 230 illustrated in FIGS. 8 and 9 is carried on barge 260 near the bottom 264. Power pack 276 provides the hydraulic fluid needed to power the cutter wheels on head 270 and the various hydraulic cylinder actuaters needed for positioning the head at an appropriate cutting location.

The barge 260 itself provides the support to the rest of the apparatus in this embodiment. Means for providing motion and appropriate positioning of barge 260 includes a number of winches, mooring lines and anchors. In particular, fore and aft winches 278 and 280 respectively are connected to mooring lines 282 and 284 which in turn are connected to anchors which are positioned in a conventional manner slightly offset from the desired location of the trench. In similar fashion, a pair of winches 286 and 288 are provided on left and right sides of the forward end of barge 260. Mooring lines 290 and 292 are connected to the winches 286 and 288 respectively and extend to anchors positioned laterally displaced from the traverse along which a trench is to be cut. In similar fashion, a pair of winches 294 and 296 and corresponding mooring lines 298 and 300 are carried on the rear of the barge 260.

The winch and mooring system thus far described provides means for both moving the barge 260 at a controlled rate along a desired traverse and also for maintaining the barge 260 both parallel to and precisely in transverse alignment with the desired traverse. Each of the winches is preferably hydraulically controlled. As a result, it is a simple matter to use a hydraulic speed control system such as that shown in FIG. 10 to drive the winches 278 and 280 to cause barge 260 to move along the traverse at a rate which will maintain constant cutting pressure on the rock cutter wheel 270.

In similar fashion, the lateral winches 286, 288, 294 and 296 may be automatically controlled to maintain precise alignment of the barge 260 with a traverse. To achieve this automatic alignment, a pair of laser targets 302 and 304 are positioned at the forward and rear ends of barge 260. Most subsea pipelines are laid out to a nearby shoreline. As a result, there is a stable ground surface available for positioning a laser light source. In this embodiment, a laser source is positioned and directed to provide a laser beam parallel to a desired pipeline location and positioned a few feet above the water surface. The laser targets 302 and 304 are then either manually or automatically aligned with the laser beam by appropriate differential control of the various winches to maintain the barge 260 in precise alignment with a desired path of operation. Differential light beam detectors suitable for use as targets 302 and 304 are well known and need not be described further here.

It can be seen that in the FIGS. 11 and 12 embodiment the transport means, which is the barge 260, provides both motion along the desired traverse and also means for providing almost perfect alignment with that traverse. The barge 260 also provides a very level base unlike the normal ground surface so that correction for right or left tilting is of no great concern. As noted above, it is desireable to provide some small amount of lateral shifting capability to the boom 264 and to provide the rotary joint in head 270 to compensate for the very small misalignments which can be expected in this barge mounted system.

Although physically quite different from the earlier embodiments, this FIGS. 11 and 12 embodiment is operated in essentially the same manner. That is, the transport 260 is used to position the cutter wheels over the surface in which the trench is to be cut and the cutter wheels are rotated and lowered into that surface. The transport 260 is then used to move the cutter mechanism along the traverse at a controlled rate while alignment of the blade with the traverse is maintained. It is preferred that the explosive cord placement arrangement of the FIGS. 3 and 4 embodiment be included in this barge mounted device. The preferred method of operation therefor includes the cutting of a pair of slots for a distance corresponding to the distance between boom 264 and the auxilary backhoe 274 at which time the explosive cord laid in that section is detonated. Cutting is then resumed while the barge 260 is moved along and the backhoe 274 is used to clear out the rubble from the section of trench formed by the previous detonation. It can be seen that is desireable to extend the length of barge 260 as much as possible so that relatively long sections of trench may be cut between successive detonations. This arrangement provides a very Rapid method for providing a trench in the rocky floor of a body of water.

With reference now to FIG. 13, there is illustrated a method of undercutting pipes and other conduits crossing the desired route of a trench. In FIG. 13, a ground surface is designated 310 and a number of conduits 312 are indicated positioned normal to the surface of the drawing. It if often necessary to lay a pipeline crossing the path of conduits 312 and generally this must be done at a lower position. A portion of a boom 314 carrying a cutter head 316 having rock cutter wheels 318 it is illustrated making a cut under the conduits 312. As is understood from the above descriptions, trenches are cut with apparatus of the present invention in a number of individual passes to reach a desired depth. The dotted lines 320 indicate the path of cutter blade 318 on a first pass which terminated short of the conduits 312 on opposite sides. Likewise second dotted lines 322 indicate the location of a second pass of rock cutter wheels 318. A third set of dotted lines 324 indicate the path of a third pass by the cutter wheels 318 which partially undercut the conduits 312 and almost formed a continuous passageway below the conduits. Fourth lines 326 indicates a final pass of the cutter wheels 318 which cut slots more than half way beneath the conduits 312 so that when the wheels 318 are also brought in from the opposite side a continuous path will be cut below the conduits 312. Due to the close control provided by the apparatus of the present invention, operators have been able to cut within a few inches of conduits such as conduits 312 without actually disturbing the overlying ground surface materials. This ability to undercut the crossing pipeline saves both time and money and avoids unnecessary damage to the crossing conduits.

While the present invention has been shown and illustrated in terms of specific apparatus, it is apparent that various modification and changes can be made within the scope of the present invention as defined by the appended claims.

Claims ( 32 )

Apparatus for digging a ditch in a horizontal surface of the earth, by means of a machine moving over the horizontal surface along a traverse, comprising:

boom means carried by said transport means having a first end articulable downwardly into a substantially vertically walled ditch cut in the earth’s surface below the surface traversed by the transport means;

rock cutter means comprising a pair of spaced rock cutter wheels each having a relatively large diameter-to-cutting width ratio adapted to cut spaced parallel slots in the earth’s surface carried on the ends of a rotatable shaft journaled in a bearing housing, said shaft carried on said first end of said boom means; and

alignment means for aligning the outer surfaces of said rock cutter wheels parallel to and between the walls of said ditch and for maintaining the cutter wheels aligned with the outer walls of previously cut slots as said transport means moves along said traverse whereby successive parallel cuts each to a depth up to the housing may be made along the bottom of said ditch after the material between a previous cut has been broken and removed to thereby extend said parallel walls to a preselected depth greater than the radius of the cutter wheels.

said transport means comprises a frame carried on a pair of tracked traction means and an engine carried by said frame for powering said traction means;

said boom means comprises an extendable boom supported on said frame by means of turntable means for providing limited rotation of said boom about a vertical axis, said boom connected to said turntable means by a first horizontal pivot having a pivot axis in the plane of said boom and a second horizontal pivot having a pivot axis perpendicular to said plane, said boom means further including means for rotating at least a portion of said boom about its longitudinal axis; and

said alignment means including control and actuator means for rotating said boom about said vertical and longitudinal axes and for pivoting said boom about said horizontal axes to align said rock cutter wheels between the walls of said ditch.

said alignment means further includes an arm extending from said frame and having a marker for alignment with said traverse on the earth’s surface, whereby said traction means may be maintained in alignment with said traverse as it moves along said traverse.

Apparatus according to claim 1 further including a hollow guide carried by said boom means and extending along the circumference of at least one of said rock cutter wheels to point spaced from a lower edge of said at least one wheel, and a supply of explosive cord carried by said boom and extending through said guide into a trench cut by said wheel, for positioning said explosive cord in said trench as said transport means moves along said traverse.

Apparatus according to claim 4 further including a crumbing shoe carried by said hollow guide for clearing loose cuttings from the bottom of said trench so that said cord may be positioned on the bottom of said trench.

Apparatus according to claim 1 further including water spray means comprising a water conduit carried by said boom and a nozzle for directing water from said conduit at the periphery of said cutter wheels to simultaneously cool said cutter wheels, suppress dust and consolidate walls of a ditch cut by said blades.

said boom means comprises a boom having a first end connected to said tractor by means of a vertical pivot and a horizontal pivot;

said rock cutter means is carried on a second end of said boom by rotation means for rotating said shaft and rock cutter wheels about a vertical axis;

said alignment means includes control and actuation means for pivoting said boom about said vertical and horizontal pivots and for rotating said shaft about said vertical axis to align said rock cutter wheels between walls of said ditch.

a track driving hydraulic motor coupled to said tractor tracks for driving said tractor, said track driving motor coupled to said hydraulic pump means for receiving hydraulic fluid.

said transport means comprises a dual tracked base, a frame carried on said base by means of a turntable for providing rotation about a first vertical axis, and engine means carried on said frame for propelling said transport means;

said boom means comprises a boom having a second end pivotally connected to said frame by a horizontal axle;

said rock cutter means is connected to said boom first end by a rotary joint allowing said rotatable shaft to rotate about a second vertical axis; and

said alignment means includes control and actuator means for rotating said frame about said first vertical axis, for raising and lowering said boom about said horizontal axle, and for rotating said shaft about said second vertical axis, to align said rock cutter wheels between the walls of said ditch as said transport means moves along said traverse.

Apparatus according to claim 10 further including hydraulic pump means coupled to said engine means, first hydraulic motor means coupled to said track means and to said hydraulic pump means for propelling said track means, and second hydraulic motor means coupled to said rotatable shaft and to said pump means for rotating said cutter wheels.

said hydraulic pump means includes first and second variable displacement hydraulic pumps, said first hydraulic motor means comprises first and second hydraulic motors coupled to said dual tracks, said hydraulic pump means further includes a third hydraulic pump coupled to said second hydraulic motor means;

further including control means coupled to said first, second and third hydraulic pumps for controlling the speed of travel of said transport means as a function of the fluid pressure at the output of said third hydraulic pump.

said transport means comprises a barge having mooring line and winch means for moving said barge along said traverse on the earth’s surface, said barge having a central opening extending from upper to lower surfaces;

said boom means comprises a boom having a second end pivotally connected to a wall of said central opening by a horizontal axle;

said rock cutter means is connected to said boom first end by a rotary joint allowing said rotatable shaft to rotate about a vertical axis; and

said alignment means includes control and actuator means for controlling said mooring line and winch means for positioning said barge in alignment with said traverse, for raising and lowering said boom about said horizontal axle, and for rotating said shaft about said vertical axis, to align said rock cutter wheels between the walls of said ditch as said transport means moves along said traverse.

said mooring line and winch means includes a forward pair of winches and mooring lines and a rear pair of winches and mooring lines, said mooring lines of each pair extending in opposite substantially lateral directions from said barge whereby said barge may be moved laterally and rotated about a vertical axis.

Apparatus according to claim 14, further including laser means for providing a light beam above and parallel to said traverse along the earth’s surface, forward and rear light beam detectors carried by said barge, and automatic control means coupled to said detectors and to said forward and rear pairs of winches for automatically aligning said barge with said light beam.

Apparatus according to claim 13 wherein said mooring line and winch means includes a forward winch and a mooring line extending generally forward of said barge and a rear winch and a mooring line extending to the rear of said barge;

said rock cutter means including a hydraulic motor for driving said rotatable shaft and a hydraulic pump carried on said barge for driving said hydraulic motor;

further including speed control means having an input coupled to an outlet of said hydraulic pump and outputs coupled to said forward and rear winches, for controlling the speed of movement of said barge along said traverse as a function of hydraulic pressure at the hydraulic pump outlet.

Apparatus according to claim 13 further including lateral translation means connecting said horizontal axle to said barge for providing limited horizontal translation of said boom relative to said barge.

A method for digging a ditch through rock like material having parallel generally vertical walls along a traverse on the earth’s surface comprising:

(a) cutting a first pair of parallel substantially vertically walled slots along said traverse by means of a pair of rock cutter wheels carried on opposite ends of a rotatable shaft, said shaft carried by a boom extending from transport means moving along said traverse;

(b) subsequently removing material between said first parallel slots by another means to provide a ditch having parallel substantially vertical walls;

(c) positioning said rock cutter wheels between and parallel to the walls of said ditch and cutting a second pair of parallel substantially vertically walled slots along said traverse by means of said rock cutter wheels, said second slots being aligned with said first slots;

A method of digging a ditch along a traverse on the earth’s surface, said traverse crossing the path of a buried conduit, comprising:

(a) cutting a pair of parallel narrow slots in the earth along said traverse except in the region of said conduit by means of a pair of rock cutter wheels of preselected diameter, said wheels carried on opposite ends of a horizontal shaft supported on an articulated boom, said boom supported by a vehicle traveling along said traverse, the length of said shaft and width of said boom being less then the spacing between outer teeth on said rock cutter wheels;

(c) repeating steps (a) and (b) until the bottom of the last-cut slots is below said conduit a distance at least as great as the diameter of said rock cutter wheels;

(d) cutting extensions of said last-cut pair of parallel narrow slots through the material below said conduits and along said traverse by means of said rock cutter wheels by articulating said boom to move said wheels under said conduit from at least one direction; and

A method of digging a ditch having parallel generally vertical walls along a preselected traverse on the earth’s surface including:

(a) positioning a transport means in alignment with said traverse, said transport means carrying a boom extendable into the earth’s surface and said boom carrying a pair of rock cutter wheels each having a narrow cutting width relative to the cutting depth and spaced apart a distance somewhat greater than the cutting width on opposite ends of a rotatable shaft;

(b) aligning said cutter wheels with said traverse and rotating said wheels while lowering said wheels into the earth’s surface;

(c) moving said transport along said traverse while maintaining said rotating cutter wheels in aligment with said traverse to thereby cut a pair of substantially spaced, parallel, substantially vertically walled slots along said traverse;

(d) removing material between said slots to provide a ditch having parallel substantially vertical walls.

Apparatus for digging a ditch having parallel, generally vertical walls along a traverse on the earth’s surface comprising:

transport means for providing support and including engine and traction means for moving said transport means along said traverse on the earth’s surface;

boom means having a first end supported by said transport means and a second end articulable into a substantially vertically walled ditch cut into the earth’s surface along said traverse;

rock cutter means comprising a pair of rock cutter wheels carried on ends of a horizontal rotatable shaft, said shaft being carried on said second end of said boom means and being lowerable into a substantially vertically walled ditch;

alignment means including means for positioning said boom second end over said traverse and for lowering said cutter wheels to cut slots in the earth and means for pivoting said horizontal shaft and rock cutter wheels about a generally vertical axis relative to the boom means to align said wheels with said traverse, and means for maintaining alignment as said transport means moves along said traverse, whereby angular and lateral misalignments of said transport means may be corrected for.

Apparatus according to claim 21 wherein said alignment means includes a vertical pivot coupling said boom means first end to said transport means and control and actuator means for pivoting said boom means about said vertical pivot for laterally moving said boom second end to a position on said traverse.

Apparatus according to claim 21 wherein said alignment means includes means for laterally displacing said boom first end relative to said transport means and thereby laterally moving said boom second end to a position on said traverse.

a generally elongate housing having a first end coupled to said boom means second end and a second end carrying said horizontal shaft;

a hydraulic pump driven by said engine and a first hydraulic motor driven by said pump, said first hydraulic motor having an output shaft coupled to said horizontal shaft for driving said cutter wheels;

variable displacement hydraulic pump means driven by said engine and second hydraulic motor means driven by said variable displacement pump, said second motor means having at least one output shaft coupled to said traction means for driving said transport means along said traverse; and

control means having an input coupled to an input of said first hydraulic motor and an output coupled to said variable displacement pump for controlling the speed of said second motor means in response to pressure of hydraulic fluid at said first hydraulic motor input.

said traction means comprises at least first and second tracked traction means laterally spaced about a longitudinal centerline of said transport means;

said second motor means comprises first and second hydraulic motors driven by said first and second variable displacement pumps respectively and having output shafts coupled to said first and second traced traction units respectively, whereby steering of said transport means may be accomplished by differentially controlling the displacements of said hydraulic pumps.

Apparatus for continuously cutting a slot in the earth’s surface, placing explosive cord in said slot, and tamping said cord comprising:

boom means having a first end supported by said transport means and a second end articulable to a position on said traverse;

a pair of spaced rock cutter wheels carried on a rotatable shaft carried by said boom means second end for cutting a pair of parallel slots in the earth’s surface as the cutter wheel is pulled behind the transport means;

shield means carried by said boom means spaced from an outer edge of said at least one cutter wheel and extending over a substantial portion of the upper half of said at least one cutter wheel to direct cuttings into a slot produced by said at least one cutter wheel; and

guide means carried by said boom means extending behind said at least one cutter wheel to a point adjacent the bottom of said slot for guiding explosive cord into place at the bottom of said slot below said cuttings;

whereby detonation of the explosive cord will selectively fracture the rock between the two slots to form a ditch with parallel side walls when the debris is removed from the ditch.

Apparatus according to claim 27, further including a crumbing shoe carried by said guide means and positioned adjacent the bottom of said slot for clearing cuttings from the bottom of said slot whereby said explosive cord may be positioned on the bottom of said slot.

Fiber rock saw. for mini trenching and optical fiber

cutting a pair of spaced apart narrow slots along said traverse by means of at least one rock cutter wheel carried on an articulated boom supported by transport means moving along said traverse;

during said cutting, guiding at least one explosive cord into a position along the bottom of at least one of said slots;

during said cutting, directing cuttings from said at least one slot back into said slot to cover said at least one explosive cord;

detonating said at least one explosive cord in said at least one slot to fracture material between said slots; and

A method of digging a ditch according to claim 29 further including repeating the steps of claim 29 one or more times until a preselected depth is reached.

simultaneously cutting a pair of narrow slots in the rock by means of a first self-propelled machine moveable over the surface and having a pair of rock cutter wheels carried on opposite ends of a horizontal shaft supported on an articulated boom, the length of said shaft and width of said boom being less than said preselected width and said wheels being spaced apart so that the outer edges of said slots are spaced by said preselected width and a substantial amount of material is left between the slots; and

subsequently breaking and removing the material left between the slots by a second self-propelled machine left between said narrow slots.

A method according to claim 31 further including repeating said steps of cutting narrow slots in said rock in the bottom of the trench using cutter wheels of the same width and spacing and removing said rock between said slots one or more times until a ditch having generally planar, parallel walls and a preselected depth is reached.

US06/103,231 1978-12-04 1979-12-13 Method and apparatus for cutting a trench through rock-like material Expired. Lifetime US4542940A ( en )

Priority Applications (11)

Application Number Priority Date Filing Date Title

US06/103,231 US4542940A ( en )	1978-12-04	1979-12-13	Method and apparatus for cutting a trench through rock-like material
JP17645480A JPS56128833A ( en )	1979-12-13	1980-12-13	Method of and apparatus for excavating ditch
GB8040049A GB2071182B ( en )	1979-12-13	1980-12-15	Digging trenches
FR8026577A FR2472058B3 ( en )	1979-12-13	1980-12-15
CH921880A CH645688A5 ( en )	1979-12-13	1980-12-15	PROCEDURE AND APPARATUS FOR THE EXCAVATION OF TRENCHES ALONG A LINE.
IT50374/80A IT1165572B ( en )	1979-12-13	1980-12-15	APPARATUS AND PROCEDURE FOR THE EXCAVATION OF DEEP TRENCHES IN A COMPACT ROCK
DE19803047176 DE3047176A1 ( en )	1979-12-13	1980-12-15	Digger
GB08321921A GB2136475B ( en )	1979-12-13	1983-08-15	Dual rock cutter wheel trencher
GB08321922A GB2136476B ( en )	1979-12-13	1983-08-15	Dual rock cutter wheel trencher
US06/614,460 US4662684A ( en )	1979-12-13	1984-05-25	Rotary rock and trench cutting saw
US06/779,148 US4640551A ( en )	1978-12-04	1985-09-23	Rock saw unit for hard rock earth formations

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title

US05/966,338 US4230372A ( en )	1978-12-04	1978-12-04	Dual rock cutter wheel trencher
US06/103,231 US4542940A ( en )	1978-12-04	1979-12-13	Method and apparatus for cutting a trench through rock-like material

Family

Family Applications (1)

Application Number Title Priority Date Filing Date

US06/103,231 Expired. Lifetime US4542940A ( en )

1978-12-04

1979-12-13

Method and apparatus for cutting a trench through rock-like material

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IT1165572B ( en )	1987-04-22
IT8050374D0 ( en )	1980-12-15
GB2071182A ( en )	1981-09-16
GB2136476B ( en )	1985-04-03
GB2071182B ( en )	1984-11-07
DE3047176A1 ( en )	1981-09-10
GB2136476A ( en )	1984-09-19
FR2472058A1 ( en )	1981-06-26
GB8321922D0 ( en )	1983-09-14
GB8321921D0 ( en )	1983-09-14
GB2136475A ( en )	1984-09-19
JPS56128833A ( en )	1981-10-08
GB2136475B ( en )	1985-04-03
CH645688A5 ( en )	1984-10-15
FR2472058B3 ( en )	1982-10-15

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Sources:

https://patents.google.com/patent/US6547337B2/en
https://www.theutilityexpo.com/news/trenching-tech-advancements-coming-to-the-jobsite
https://www.electriciantalk.com/threads/trenching-through-coral-rock.285133/
https://www.google.com.pg/patents/US4542940

Electric Saws advancements, coming, tech, trenching

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Trenching Tech Advancements Coming to the Jobsite. Rock saw trenching

US6547337B2. Trencher with foldable rock saw wheel. Google Patents

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Cited By (7)

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Trenching Tech Advancements Coming to the Jobsite

Smarter, more automated trenching

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Trenching through coral rock

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gpop

MHElectric

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micromind

splatz

US4542940A. Method and apparatus for cutting a trench through rock-like material. Google Patents

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DM Civil’s Tesmec TRS 1475 Trenching Rock Saw

Claims ( 32 )

Fiber rock saw. for mini trenching and optical fiber

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